Gas engine



AP 2, 1946. H. scHREcK 2,397,511,

y GAS ENGINE Filed July 11, 1941 s sheets-sheet 1 ATTOBNEY- April 2 1946# H. scHREcK 2,397,511

GASENGINE Filed July 11, 1941 5 sheets-sheet 2` 1NvENToR.' HENRY ScHREcK AT TQR NE. Y

A APY 2. 1945- 4H. scHREcK v 21,397,511

GAS ENGINE Filed July 11, 1941 5 Sheets-Sheet 3 INVENTOK HENRY. Scl-RECH ATTORNEY April 2, 1946. H. SCHRECK A '2,397,511

GAS4 ENGINE Filed July 11. 1941 5 SheefSShee-i'. 4

HALF ofw FlG.ii.

. l mvENToR FIG.12. l l BY HENRY SCHRECK APril 2, 1946 H. scHRECK I 2,397,511

ATTORNEY Patented Apr. 2, 1946 GAS ENGINE A Henry Schreck, Beloit, Wis., assignor to Fairbanks, Morse & Co., Chicago, Ill., a corporation of Illinois Application July 11, 1941, Serial No. 401,884

3 Claims.

This invention relates to gas engines, and more particularly to methods of and means for proportioning air and gas i-n a mixture thereof for combustion in internal combustion engines of certain types in which a considerable excess of air, over combustion requirements, is desirably admitted to the cylinder prior to combustion. An example of this practice is found in prevalent types of portscavenging engines, wherein the cylinder is desirably sweptV by a full charge of air for scavenging purposes, prior to compression.

Since the types of engine to which the present invention is applicable, are exemplied by two cycle, port-scavenging engineabut. since the invention. may also be embodied in engines of other types wherein an initially larger charge of air is introduced than isy usually necessary or desirable for combustion, the reference herein to engines of two cycle type s to be understood as explanatory, and the phraseY used for brevity, rather than with any intent. to restrict the present developments specically as to field of application and usage.

The invention is believed best understood by a brief reference to the nature of the problem encountered and the manner of its solution by present developments. Particularly in engines of two cycle type, difliculties have been experienced in attaining a satisfactorily low coeicient of speed fluctuation, particularly under light-load and noload. operation. Inalltwo cycle gaseous fuel engines: heretofore available to the trade or otherwise known to applicant, operation may be fairly successful and reasonably satisfactory under conditions, for example, of three-fourths' normal rated loading or higher. Such engines however fail4 utterly of attaining. a satisfactory coefficient of speed iiuctuation, or any dependable regularity of ring in the lower load ranges, for example, below one-half or perhaps three-fourths load, depending upon size and exact construction of engine.

The diiiiculty last' noted has been found by applicant to be due to poor proportioning of fuel and air, in that there has existed prevalently an improper ratio of fuel to air. More usually inthe older and prevailing types` of two cycle engines, this condition has existed primarily because of an incorrect proportioning of air charge, either or both to the gas charge and to then-prevailing engine loading. Because of this prevalent shortcoming, two cycle'gas engines have long been considered unsuitable for use with any form of connected load which isfatl times. required to operate appreciably below the normal rated maximumengine load', and which connected load is inherently such as to require a minimum fluctuation in speed from that currently predetermined, or otherwise expressed, is such as to require a minimum coefcient of speeddiuctuation. It has furthermore now been deiinitely established that gas engines, in distinction from internal combustion engines of liquid fuel type, whether utilizing fuel injection systems of so-called solid injection type, or utilizing a carburetedvapor, are much more subject to misring because of incorrect or improper air-fuel mixtures, than are internal combustion engines of the last mentioned types. Accordingly, the successful solution of the operational difficulties noted must include provisions for an accurate metering, particularly of the amount of air present just priorto combustion,and an equally accurate coordinated metering of the fuel supplied for combustion. Thisregulationmust moreover lbe such as to result in a proportion of air and gas to each other, and a proportioning of each fluid to the then-prevailing engine load conditions, such as to bring the mixture with deflniteness and certainty within thev ignitable limits, or the limits of inflammability, of fuelair ratio-s, throughout the full loadv range of the engine. The latter, it may be noted, is herein taken to include a lower limit of zero loading or idling condition ofthe engine, and an upper limit which is at least the normal full rated loading o-f the engine, even preferably including overloads-ofthe order of twenty percent.

The invention accordingly has as its general and principal object, the attainment ofl an improved method of and structural arrangement for proportioning a gaseous fuel and air, both as to their mutual ratio, and each as to then-prevailing engine' load conditions, in such manner as to result in dependable regularity of ring, and al dependably adequate coefficient of speed fluctuation, throughout the full loadrange of the engine.

objectively a most important feature of present developments is an improved method of and means for measuring in the cylinder,l a volume of air, or air charge, whichwhen admixed with a metered charge of fuel, will result in the aforesaid operational advantages.

In comparison with four-cycle engines, all of the two-cycle gas engines heretofore available to the trade have been characterized by a marked tendency to misilre when operated appreciably below rated' load. Thisadverse characteristic has been overcome, in a certain measure, but with only indifferent success, in certain types of two cycle gasengines wherein, for example, a

under comparable operating conditions.

.the gas-air charge.

f differing engineload conditions.

improvements also objectively contemplate not small igniting charge of liquid fuel is injected with the gas. Such expedients obviously increase initial cost of the engine as well as its expense of maintenance and requirement of service attention. It is accordingly a further and important object of the invention to realize a novel type of two-cycle gas engine which offers all of the advantages of four-cycle gas engines, and yet retains all of the many advantages of those of twocycle type, such as fewer parts and lesser maintenance attention.

Akin to and in keeping with the foregoing object, an important result attained by the present method and structure is found in engines of two cycle type, operating on anyof a number of true gaseous fuels (as hereinafter dened) and which While possessing the mechanical simplicity and freedom from service attention ,ofV a two cycle engine, has demonstrated in commercial service a fuel economy which compares more than favorably with four cycle engine fuel consumption Stated in terms of structure and method of operation this result, attained'for the rst time in a commercial engine operating 'on a true gaseous fuel, is due in ff i only a variation in rate of gas influx, and an earlier or later beginning of gas introduction, but a differentially variable timing of the termination of gas introduction to the cylinder.

Expressed in terms of structure presently preferred to attain the operational objectives above noted, is an improved system of valve operation and control, the valves and valve-operating agencies being such as to attain in a simplified manner and under a great variety of vengine operating conditions, a proportion Vof air to gas, which is always within limits of ignitability, and which4 `are yet safely between those high and low ratios which define the limits of inflammability of the gas utilized. 1

' description of an engine and method of operatcontributed to by strict avoidancek of any com- Y or metering the air charge in the cylinder of the( engine through a wide or substantial range of air amounts or volumes, in order to care for conditions prevailing through the entire engine load range.- The preferred and most advanced practice of metering air for the purpose noted in attainment ofthe present object includes an air volume regulation and means for effecting same bythe release orV discharge of any air which is in excess of that required for combustion under then prevailing load conditions, such excess air being a. portion of .an initially plenary volume thereof, In this manner the'airvremaining in the cylinder priorto ignition, hence prior to combustion is, if necessary, reduced to such a volume or amount, as lwill result in easy and certain ignitibility of The greatest nicety of air metering in accordance `with present improvements also involves a variation in timing, in respect to enginecrank travel, ofthe agencies by which a portion of the initial air charge is released from the cylinder; a regulation also of the rate of air egress during the step of reducing, if necessary-.the air volume to bring it safely withinl the limits, in respect to the gas charge, ofy certain Vignitability, and the completion of air metering and final establishment of the then-correct air charge, preferably wholly prior to the introduction of any gaseous fuel, and substantially prior to ignition of the cylinder charge.

,Yet another object ofthe invention, more particularly stated in reference to the apportionment of gas fuel charge, may be noted as attained in provisions for introducing the gas chargeiearlier or later either in reference to piston stroke or crank travel; the provision of means for regulating the rate of gas introduction tothe cylinder, such rate beingl desirably variable under The present ing same, particularly when considering the description in connection with the accompanying drawings, in which:

Fig. l is a side elevation-partly in section, of a portion of a two cylinder two cycle, port scavenging engine adapted to operate in accordance with the principles of the present invention, and embodying control and .other structural assemblies thereof, the sectional portions of Fig. 1 being taken in a vertical plane axially of the camshaft; Fig. 2 is a horizontal'sectional View, fragmentary in nature', of a cam followerr assembly associated with one of the engine cylinders and as viewed along line 2-2 of Fig. l; Fig. 3 is a partial end elevation of a vertical engine embodying present improvements, withv certain portions sectioned along ajvertical plane for'clearness of illustration; Fig. 4 is a fragmentary vertical section through 'the upper portion, head and valve assemblyof a cylinder of the engine shown by preceding gures', and as viewed along line 4-4 of Fig. 3; Fig. 5 is an isometric view or perspective elevation of one kof the air-release valve operating cams and a companion gas-admission control cam in an exemplifying form; Fig. 6 is a top or plan `View vof the cam assembly shown by Fig. 5,

iniorderbetter lto illustrate certain features :ofY

the lobe portions of the cams; Fig. 7 is an end elevation of the gas admission control cam, as viewed along-line 1 1 of Fig. 6; Fig. 8 is an end elevation, partly in section, of the air release valve control camas viewed-.along line8-8 of Fig, 6; Figs. 9, 10'and `11 areillustrative sector diagrams showing, in reference to differentY angularV positions of theengine crank, the-times Vof opening and closing of the airgrelease valve and the gas admission valve, hence indicating the angular periods, expressed in terms of crank angle, through Whichair release for combustion airV proportioning purposes takes place, and the angular periods through whichA the introduction of gasoccurs, Figs. 9, 10 and 11 Ybeing applicable, in order and asdesignated, to no-load, one-half load and fullloadv vconditions of the engine; Fig.' 12 is an isometric 'view of aislightly. modified form ofY airreleasejcontrol cam; Figs. 13, 14 and 15 constitute a group ofrelatedidiagrams showing cylinder positioiis .of the piston in relation to opening and closingL times of the fair and gas valves, Fig. -13 showing lin full lines the piston position at the beginning of gas injection, while Fig. 14 shows a position of the piston near top dead. center, and

Fig. 15 showing a pressure card or diagram on which is superposed `an indication of time of the various valve opening and closing events, the three ngures of this .group yall relating to no load engine operating conditions; Figs. 16, l-'l and 18 correspond, as a group, in nature and purpose,'respectively vto Figs. 13, 14 and 15, except showing piston positions, valve events, and exemplary cylinder pressures under conditions of full rated engine load, and Figs. 19, 20 and 21 constitute -a group corresponding in nature and purpose to Figs. 13, 14 and 15 respectively, but show piston positions, valve events and exempiary vcylinder pressures under conditions of 120% rated load.

Before describing by characters of reference a selected embodiment of the invention in a portscavenging I'gaseous ,fuel engine, it should rst be stated that the expression "gaseous fuel as utilized in the present disclosure and appended claims, has reference to any fuel of .a type which exists and remains until burning, in a gaseous, as distinguished from vaporous or liquid condition, throughout all lreasonable extremes of temperature. Otherwise defined, for purposes of present description land claims, a true gas, or gaseous fuel, maybe considered as a fluid which, under ordinary :ambient pressures and temperatures, has neither independent shape nor volume, but tends to expand indefinitely. (Webster.) By Way of vstill further definition, the substances to and with which the present engine developments are applicable, consist of those gaseous substances suitable for internalA combustion engine fuels which are composed for the greater part, say at least 95%, of an ingredient or ingredients having a molecular weight not exceeding 75. This deniti'on Ais to be understood in connection with the present description, developments, and in the appended claims, ito embrace gases of xed formula'e and composition, or `mixtures thereof, as well as 4industrial or other kgases usually composite in nature; it being the intent of this definition to include therein those fuels which, within the range of atmospheric temperatures encountered in the United fStates, and vat atmospheric pressures, Vnormally exist and are :or may be commercially handled as gases, in distinction from liquids and solids, in the sense that true gaseous fuels are understood in present accepted or developed meaning, lby those particularly skilled in the -art of -'gas engine design and operation. As typical of fuels of .gaseous type contemplated in connection with present improvements, there may be mentioned fas illustrative, but not as exhaustive, those .ranging from, say blast furnace gas up through fgaseous ifuels of Vthe highest caloric value. '-Ihese include illuminating gas whether coalrgas, waterzgas or mixtures of same; so-called bottled `gases, natural gases, and many others. The engine illustrated, since the drawings are partly taken from an operating engine, may be noted as designed particularly for and as having most successfully operated on a fifty percent dilotion 'of butane. The latter in .pure state, having a caloriiic value approximating 43000 B. t. u., the engine seiectedfor description :has been successfully operated ongas of the caloric order of 1500 B. t. u. It iste be '-noted, however, that merely by lchanging -or substituting cylinder valves v,and

valve cagesy of greater or less diameters, the engineis easily adapted 'for the use of fuels oisreaterfor less. heat value. In order still further to attain a. better understanding of the principles underlying 'the ypresent improvements, it should be stated that the difficulties encountered, and the solution thereof which .resulted in the present developments, are chieiiyithose attending the use of a gaseous'fuel ina'n internal combustion engine,.particularly one of Vport scavenging type. This fact is'noted inasmuchas certain sporadic attempts have experimentally been made heretofore, to vary the volume of combustion air, in two-cycle vDiesel type engines. Such attempts have led to no :useful result, since an excess of combustion Yair is not only no disadvantage, but is in fact a desideratum in Diesel operation wherein it :is desired to assure full or nearly full compression vpressures under all load conditions of 'engine operation. Such yfact arises in part out of the `necessity for maintainingat all times, a full cylinder-charge, in order to insure dependable compression ignition. Furthermore, and very importantly, it is to be noted that in Diesel operation, compression pressures being high enough to insure ignition, anda liquid fuel being employed, there will 'always obtain in some localized portion of the fuel spray-'and fair intermixed .therewith, a 'charge-kindling condition. This relation of `fuel and air does Knot at all obtain with any uniformity lin conventional gaseous fuel engines. Both fluids 'present being distinctly gaseous vin nature, the relatively I'quick diffusion of gases occurring in the cylinder causes immediately upon introductionof Igas to 'thecyiinden in case an excess of air be "present, an air-gas mixture which is too lean to ignite, this condition being particularly prevalent lai; lighter loads, since, a lesser gas charge :being present with the maximum cylinder -volume of air, the proportion of gas to air fails even to attain the lower percentage of ignitability.

VProceeding now to describe the engine selected as an example to utilize present improvements, while portions of the engine may be of' conventional or other suitable type or form, for completeness of description a. .portion of the crank case is indicated at 2D in which revolvably operates a crank shaft 2l provided with a crank 22, a conventional `or other suitable rod 23 being connected .through a wrist or piston pin (not 1 shown) to piston n21.9 The latter reciprocates, according-to Well known practice, in the cylinder structure 25 provided with a cylinder head 26, and if electrical ignition be employed, igniters or sparkplugs 30 are used, 'there being one or more per cylinder.

Shown asopening inwardly of the head 26 of the-cylinder and into Ithe combustion space 3l, is a gas admission valve 32, engaging a suitable seat 33 and provided with vanelongate valve stem 34 and valve seating spring 35. It will be noted that the valve 32 controls the opening and closing of a gas admission conduit 36 connected with a suitable supply fof gas (not shown), if necessary, through a gas pump (not shown) in a line provided optionally with a `gas pressure regulating valve (not shown) in case .a high pressure gas source-isutilized.

Arranged somewhat similarly to the gas admission 'control valve '321, ris an air outlet valve or release valve, preferably considerably larger in diameter vthan the va1ve..32, and indicated at 45. The1air-valve,socalled for convenience and brevity, coop'era'tes with .a seat '46 in `controlling 4 e Y :2,397,511l

andm'etering a relief flow of'airoutwardly from the cylinder space 3l, as .will later better appear. Y

The air valve 4-5 is also provided with a valve stem 41 and valveispring 50 tending, likeV spring 35toY .urgethe associated ,valve into closed position.Y M, .Y

The valve actuating gearvincludes, f or each of the valves-32 and 45,.,arockerarm 5|providedv with a -tappet roller 52 engaging' the upper or Y outer end of the valve stem to which it is related. EachV rocker arxnis suitably fulcrumed as Yon a pin 53 carried by a stand 54 in turn secured to Y the cylinder head 26; Vthe opposite end of each rocker 5| is provided with a threaded adjustingy more fully described.

The outer free end Iportions or arms of the `yoke 53 are apertured to receive a stub shaft or axis pin 1I pinned .as by a key 'I2 so as to retain vthe element 1| in axial position and against rotation inthe yoke. vThe stub shaft 1I ofA each follower assembly servesfto carry a pair rof follower rollers 13, each roller 'l3rrbeing journalled and freely rotatable on the` element H and similarly free axially movable along this element for a purpose later appearing; Y

It will best appear from Fig. 1 that one of the follower rollers 13 is provided foreach cam of the pair provided for each cylinder, only one cylinder being shown for simplicity of'illustration. For general completeness of'present vstructure the camshaft is indicated; generally by the numeral 14, and alongside each cylinder of the engine, if there be more than one, the camshaftcarries, rotatably secured thereto, an, air-release or airmetering cam l5 and a gas-admission control camfl, the profiling and features offwhich Vwill be hereinafter describedin more detail. Since the present disclosure illustrates agtwo-cycle engine, the camshaft 'I4 willv b'e'driven at crankshaft speed asV by` any suitable or conventional operative connection to assure correcttiming of the cam.V

shaft at'all times. Illustrative of a suitable camshaft drive,'is a sprocket 'il on the camshaft, and a similar vsprocketll on the'crankshaft, the sprockets being operatively connected by a timing chain 8l.` if Y For'furth'er completeness of description in the example selected, it is noted that the engine is provided with a governor 82., Yequipped with aA n beingV secured to androtatable with V`the cam shaft 'i4 as by a `key or the like (not shown).

Cam shaft bearings of any desired form are pro vided within the housing 55-61 and are indicated at 90..v

lOn the Vend of camshaft *opposite the sprocket 11,- is'anjigni'tiontiminggear 9| meshing'with unitneed'beV provided only in the event electrical".

ignition is employed; if this, kbe battery ignition, the-unit Y94 may consist of .a breaker, distributor and coilassembly, or in assembliesY without battery current available for ignition,;,the,.unit may .consistjof a magneto, a number of suitable types Vof which are known in the trade and re-.

Vduiregno detailed description.V If dual ignition be employed, a pair of the unlts-94 may beoperatively vassociatedv with rthe gear 9|, as will ,be readily apparent. I Y

As to ignition instrumentalitiesfotnerthan,the v device S4, these are or` may be of -any suitable orconventional form. Ignition timing willrdeypend upon the speedrange of the engine, and perhaps other characteristics, but a present preference is to cause ignition within a range of 40.

Vto 25' ahead of top centerv piston position,ia`s indicated onrthe diagrams of Figs.`9, 10andl11.'

The'general principles involved in the control of the fuel admission and air relief Vvalves, in response to varying load conditions of the engine affecting the governor B2, will be vgenerallyapparent by noting that there are provided for each cylinder Vof the engine at least a pair of rotatable cams; that each of these cams is of a substantially greater axial extent or. lengthalong. the

camshaft, than is the'co'operating follower ele. ment associated with each of these cams. YEach of the cams being of varying `effectivecontouring in different axial Zones, it becomes apparent that since the control element of the'governor' is operatively connected tothe followers to cause acoordinated axial displacement thereof, a suitable load regulation is attained. The structural details of an exemplary embodiment of this Vassembly areY hereinafter discussed in more detail.

Proceeding now to a more detailed discussion of the presently preferred cam profiling or contour, and the elements cooperatingk therewith for governed control of gas admission and air metering, vit should rst be noted that inthe selected example both 0f the paired cams for `each cylinder indicated at and 16,'are axially and angularly secure-d to cam shaft 14 Aand hencethese two cams are'in constant phase relation."y With particular reference'to Figs. 5 and 6 it lwill be noted that each ofthe cams i5 andfl is by preference formed, as to the major part of its surface,

y o n a'base circle, from Whichit results that the major area ofeach cam, engageable by its asso-f4- ciated follower rolleris in theformof a base cylinder. To produce the; camnaction desired to carry intoV effect the principles and'methodv of operation,` it will appear that the air cam 15 is characterized by a lobe portion, or follower-actuatingareasuch as the projection generally indicated at l0. It willV of course be understood YVthat according to arrangement of valve andvalve operating mechanism, the follower-actuating portionV I maybe depressed below the basecylinderghence characterized or generated :by nega# tiv'e rather than positive radial yincrements ,of

the basecylinder surface. Thelobe V'l 00 `as shown,

isd'ened; in its portion rst'engaging the associated follower roller, by 'a substantially'retti,

linear zone IUI whichis crosswise' ofthe cam"Y or' substantially --parallel to thecam axis. 1 In plan, thel'obe -Itlisv incompletely triangular in outline if deveoped to a'planar structure,`fso` that its followeraleaving edge, indicated at 1102,-.may beregarded'as a rectilinear, zone.' lying' at 1 an acuteVV angle fto the camA axis. The intervening lcbe'orfollowerfactuating arearis thus of sub-A stantially greater-width'ongone side of the cam' thanonthe other.; Eurth'ermoraasfwill readily.`

appear from Fig. 5, the radial increment resulting. in the wider side of the lobe is similarly greater than the radial increment which results in the shaping of the more narrow side of the lobe. This results in a lobe portion of tapered depth from what maybe called the light-load side of lobe |00, which slopes downwardly or inwardly, to the heavy-load side of the lobe.

Referring now to the gas-admission cam 16, this too is characterized bya basic cylindrical portion constituting considerably the greater part of the periphery of the cam, and is modied by varying radial increments proceeding axially of the'cam, to constitute the lobe or area |03. This cam follower actuating portion is bounded in the portion rst engaging the follower, by a rectilinear zone |04 which is at an acute angle to the earn axis, and on the opposite or followerleaving margin of the lobe by a similar rectilinear zone |05. It is here noted that the zone |04 is, by great preference, exactly parallel to the zone |02 of the air release cam. It will be noted however, that the margins |04 and. |05 of lobe |03 are not parallel, from which it results that what may be termed the heavy-load margin of the cam is of appreciably greater angular extent, so as to provide, as will appear, for a longer lperiod of gas admission expressed in relation to linear pistontravel or degrees of rotation of cam or crankshaft. There is also by preference, a slight difference in radial increment resulting in the height or depth of lobe' |03, between its heavy load and light load ends. As will appear also from Figs. 5 and 6, the major portion of the effective surface of lobe |03 is in the nature of a plateau, so that when the gas cam follower engages lobe |03, it is held'at full-open position during substantially the greater part of its opening period.

Referring again to the air-release valve cam, it is further to be noted as a distinct preference, that the follower-leaving portion or zone |02 of the lobe |00 is such as to provide ar relatively abrupt shoulder in this zone, from which it results that, as will later appear, at the end of the air metering or air release operation of valve 45, the. latter closes extremely abruptly. This is advantageous to prevent trickling of the outward moving air stream, which would result in inexact metering and a varying remanent cylinder air charge.

With reference to vthe means by which the governor 82 through its regulating function, vis brought to affect the air-metering cam-andvalve assembly, and the fuel-admission camand-valve assembly ofk each of the cylinders, it may be noted that the governor is preferably of a type susceptible of various speed settings as indicated for example, by the governor speed control lever H0. While the governor 82 may be of hydraulic, centrifugal, or other suitable form, it will be noted that the regulating effect of the governor, in its response to uctuation in engine loads for a given governor speed setting, is reflected in a rocking movement of the regulating lever 83 about its pivot 84. Through a connecting link |I| pivoted at one end to the arm or lever 83, this movement is imparted, through a pivotal connection H2, to a reciprocating regulating movement of a follower control rod H3, the rod H3 being supported for reciprocal movement, in bearing arms or the like H4. The rod H3 carries in the manner best appearing in Fig.' 2, a plurality of'small yokes H5, each secured as by a setscrew H6 to prevent axial displacement of the.` yoltesV on the control rod H3 as the latter is axially moved under the regulating action of the governor arm 83. It will appear that the inner face portion of each of the yokes H5, is cut away so as to provide a pair of oppositely disposed arms, partly yet loosely embracing the periphery of the associated camy follower roller 1-3. Through the interengagement of each yoke H5 with a roller 13, it will appear that, as the control rod H3 is shifted under governor action, it. will serve to shift,'to the same extent, each of the cam follower rollers 13, in one direction or the other, axially of the several cams 15 and 16. Because of the differing proles. of the cams in their several transverse sections, it Willv be seen that, responsive to diiferent engine load conditions, the follower rollers being of considerably lesser width or axial extent than their cooperatingv cams, the governor regulation will result in tending to maintain the speed-of the engine by metering a charge of less air in the cylinder, and a correspondingly less gas. charge in one direction of regulation, and metering an increased air chargeremanent in the cylinder for combustion and a correspondingly greater gasl charge responsively to regulation with opposite effect.

Although the essentials ofthe method of proportioning both combustion air and gasv charge, to then prevailing engine loading, will have been apparent from the foregoing description, it may be further noted, most. readily from reference to the sector diagrams of Figs. 9, 10, and 11, and that while these are to be understood as illustrative rather than restrictive, the diagrams, collectively considered, will provide the angular limits between which, according; to engine load, air release begins for metering purposes, and likewise, will graphically show the angular limits within which the valve 45 closes,Y and thus air release is terminated, and the metering operation finally completed. There will similarllr appear from the sector diagrams, the angular limits expressed in terms of crank, travel on compression stroke, in which gasA introduction or injection begins, and in thesame fashion the crank angle limits under different load conditions within which gas introduction is terminated. In order to render even more graphic the relation of piston positions to gasv valve and air release valve events, these are directly shown in diagrammatic form by figures numbered 13 through 21, being in groups of three figures each corresponding to no load, full load and load. I

In order to renderv more meaningfuly the sector diagrams of Figs. 9, 10 and 11, it may be noted that each of these showings represents the opening and closing time, expressed; in` reference to crank angle position or movement, in the. compression stroke of a two-cycle port-scavenging engine. It will' be. understood of course that ignition takes place through one or both. of the plugs 30, when the piston. 24 is atv or somewhat ahead of top center position, valves 32 and 45 both being closed, and the expansive. force of the burning charge withinr cylinder space 3|, operating to impel the piston 24 on its; inward or working stroke. It will be understood of course that the head of piston 2,4 when the latter is at inner or bottom center of the working stroke, serves to uncover or clear an air supply port |20 and an exhaust port.A IZI, each of these ports being provided with the usual communicating port passage as shown.. As soon as the piston has uncovered or opened ports |20 and |2| substantially over their full areas or an appreciable portion thereof, the opening of port |20 permits a rapid ingress of scavenging and combustion air which first clears the cylinderV space 3| of` spent gases, expelling same through the exhaust port |2| and leaving the cylinder space 3| lled or substantially lled with its full capacity of fresh combustion air. Y

As the piston 24 again ascends, and covers ports |20 and |2I there is entrapped ahead of the pistonA a full charge of fresh air. However, at about this time, the cam Yfollower roller 13 rst engages the zone ofthe lobe |00 of air release calm 15, opening valve 45. The piston now moving toward the cylinder head in an upward or outward direction, continues to expel a portionof the air.until such time as the'valve 45,y

closes as determined by the time when the cooperating follower rollerv 13 moves off of the abrupt'shoulder in'zone'l02 of. cam lobe |00. This time of release valve closing, as will have appeared and later be discussed, is variable according to load. l

Immediately or only slightly after the air release valve 45 is closed, as above described, it will appear that the follower roller 13 cooperating with lobe |03 of cam 16, first engages the zone |04 vof lobev|03 andthe gas valve is initially opened. The gas being supplied by the gas pump or otherwise under substantial pressure suili-` cient to impel the gas into the cylinder under any degree of compression, is injected into the cylin der for va duration measured by the transverse extent ofthe cooperating portion of gas-camactuating lobe |03 on cam 16, gas injectiontermihating when'the gas-cam follower-roller leaves the zone|05 through rotation of cam 16. VThe duration of gas admission valve opening is Avariable according'fto load, las will have appeared. The extent of valve'opening is also variable according to`diiferingYloadconditions of the engine as has Ibeen mentioned heretofore, and because of the bias relation of zonesY |04 and |05 with respect tothe axis of cam rotation, the timing of both opening and closing of the gas ad-` -mission valve is variedY according to the existing axial position'of'its cooperating follower roller andY hence isV different vin accordance with differingV engine loads. This difference is graphiin the cylinder, until after closing of valve 45,l

- three pressure diagrams, Figs. l5, 18 and 21.

To describe in some furtherrdetail and to en# able a better visualization of the differenceA in functional relation of the different portions of the cam lobes |02 and |05 and their respective followers 13, reference is particularly directed to Figs. 5 and 6. In th'e latter figure suitable legends and small solid line arrows indicate with respect to each cam, the direction of axial displacement cf cally indicated by a comparison of the lesser and' greater periods of gas Yinjection apparent from a comparison of Figs. 13 and 19.

Air now having been accurately metered in the cylinder by releasing an accurately predetermined amount from the initially constant cylinder volurrie,thereremains an amount correctly proportioned to then-existing engine load condi-` tions, 'and the gas having beenjust admitted and proportioned to the amount of air in the cylinder as the piston approaches or attains its top center position, the charge vis ignited either electrically through plug 30,'or by h'eat of compression, or otherwise. now burningrcharge in the cylinder, again impels the piston downwardly during the power stroke of the engine in general accordance with' recognized Htwo-cycle operation.

' I tvwill have appeared Vfrom the foregoingfdescription and the relation vof the air release cam lobe|00 to its follower roller, thatl closing of the air release'cam 45 takesplace at points in piston travel :during the compression stroke which are variable according to load conditions. Since there isno effective compression of the air charge As well known, the expansion of the f the cooperating follower 13, toward the Vleft in the figure as engine loadingincreases, and toward the right in the ligure as lighter loads are imposed on th'e engine. The extreme right hand peripheral portion of each' cam (Fig. 6) may be taken as representing a no-load or ,negligible load. Although it will be understood that the followers are reciprocated in substantially the same vertical plane, having only asmall arcuate movement, it is believed clearer to consider the relative movement of followers with respect to cam lobes as taking place inthe direction sh'own by dotted arrows in Fig. 6. It will have been noted from Figs. l and 2, that the follower V'rollers 13 are characterized by aconvex periphery', from which it results that the actual area of engagement of each' follower with its cooperating cam, is little more lthan a point contact at aV given instant. This fact, considered with the variation of slope in several directions, on each of the lobes |00 and |03, will account in part for the nicety of regulation actually attained in practice.

By way of example let it be supposed that the cams are in rotation during engine operation and thatl the follower roller Vacting on the air release cam, under light or zero load conditions, approaches ythe zone |0I, is there gradually lifted, shortly thereafter is" lifted to, or nearly toits maximum extent, thus opening the valve 45. 'I'he follower, thereafter riding on the longest por-y tion and the deepest portion of lobe |00,.wi11 be held open to its full maximum, for the'maxiinum interval, expressed in termsY of crank angle,`thus releasing the maximum volume of air and metering the air remanent in the cylinder to the minimum desired for zero ,or substantially light load operation. When the follower roller leaves lobe |00 in the zone |02, an abrupt termination of opening of valve 45 takes place because of the relatively sharply shouldered shaping of zone |02, this quick termination making for most accurate metering. x Y Y Y Considering the air release valve operation in the other extreme engineloading, it will be noted that with' the follower engaging the left hand portion (Fig. 6) of lobe |00, the air release valve will begin to open at the same time as under th'e preceding condition, but willV be held open for a duration, in terms of crank angle, which is at a minimum. A minimum of air thus being released, nearly a full cylinder charge will be retained. Termination of air release is equally rabrupt as above described. It will be noted that the relatively shallower portion of lobe |00'near the heavy load end of the cam results in airV emission at a somewhat `reduced rate, because of the lesser extent of opening of Valve 45. The zone 02, being rectilinear in form' although biased with respect to the axisrofcam revolution, will result in an optimum -variation in extent of air released, between light load and heavy load conditions as graphically represented, and as will further appear from the shaping of the lobes as illustrated.

Th'e action of the gas-cam-actuating portion or active profile |03 thereof on its follower element is somewhat the same as heretofore described, withv the important exception that the zonel |04, being'v sloped or biased with respect to the cam axis, results in an early and late valve opening effect according to variation in engine load. The effect of this is readily apparent from the' differing stroke lengths of the gas injection arrows-shown by Figs. 13, 16 and 19. It will be Q15 noted also that while there is preferably a slight difference in radial depth of the lobe |03, or radial increment kof cam- 16 from end to end of lobe |05, this. differenceis vonly slight, and not nearly as marked asin the case of vlobe controlling the air release valve. It will have been apparent that as aresult of thisgreatly differing depth of lobe. portion |00, there exists a considerable difference in rate of release of air, between no-load and full-load conditions, whereas the difference in rate of gas introduction is much less marked between no-load and heavy loading of the engine. It is of advantage however that the contouring of lobe |03 be such that it exhibits wh'at may be termed a plateau over the greater portion of the lobe or active surface. This profiling is obviously such that the gas admission valve is soon brought to full-open positon, is held there for th'e greater part of the angular duration represented by distance between zones |04 and |05, and again brought to closed position.

Since in the example illustrated the followers 'I3 operate on an axis which is parallel to that of the camshaft, a straight line may be drawn parallel to th'e camshaft axis and intersecting both of the lobes |00 or |03, thus indicating, since the cams are fixed phase relation, the relative timing of the valves 32 and 45 as to opening and closing at any time during the compression stroke.

The description of a somewhat modified form of air release control cam as shown by Fig. 12, has been deferred until the present portion of description for a better understanding of purpose thereof. The modified form of air release cam is indicated at A, and corresponds in all important respects, with one exception noted hereinafter, to the structure and profile formation of cam 15, the general purpose of operation of cam 75A, being likewise similar to that of cam 15. In the modified form the several features of structure heretofore indicated and described in reference to cam '15, bear the same reference numerals in respect to cam 15A, with the addition of the suffix letter. The noteworthy difference between the principal and modified showings lies in the fact that, in Fig. 12, the lobe area or profile portion 00A, is of slightly lesser axial extent than is lobe portion |00. It will appear from Fig. 12 that the active profile area |00A terminates somewhat inwardly of the heavy-load margin of the cam 15A, thus resulting in a marginal portion characterized by the absence of any prole or contouring but consisting of a portion formed on the cam base circle, through a full 360 degrees. From the foregoing description of the regulation afforded by cam 'l5 it will appear that in case cam 15A be substituted therefor, the heavy-load margin of 15A will, when engaged by the companion follower roller, result in no lifting Whateverf 'the airreleasevcam, thus providing, as may be desirable in certain engines, an effect under full load or overload engine conditions in which the full initial cylinder volume of air is retained for combustion purposes. It is to be noted, however, that when the follower which coacts with cam 15A, is, by governor regulation, brought over the lobar area |00A, the function of the modified cam and follower on the air relief valve is the same as heretofore described in reference to cam 15.

Although some minor modifications of the lobe orprole portions |00, |00A and |03 may be made to care. for gases of different burning characteristics, andr engines of different operating requirements, the principles of shaping the active cam portions to lresult in the described method .of operation, particularly as to proportioning of gas and air, may remain essentially the same irrespective of changes in engine speed range vor other operating conditions, and irrespective of `changes in gaseous fuel, the latter being compensated for as heretofore briefly mentioned, by substitution of differing sizes of valves 32, seats 33, and cages or head structures.

The specific reference to a preferred embodiment is not to `be understood as limiting, but merely as illustrative'v of the structural possibilities within the appended claims; however, since the present improvements are peculiarly applica- ,Y ble to true gas engines, being those operating primarily on permanent fuel gases, such as natural gas, illuminating gas, bottle gases, or producer gas among other true gaseous fuels, it is intended that the present claims shall relate solely to gas engines as hereinbefore defined. Accordingly, there are hereby diclaimed any and all engines, the principal sources of fuel of which are carbureted or vaporized fuels or air mixtures thereof, or injected liquid fuels.

I claim as my invention:

l. In a gas engine of two-cycle type, a cylinder, a piston therein, said cylinder having an air admission port and an exhaust port opened and `closed by the piston, a gas admission valve, means for supplying to said valve a true gaseous fuel, an air metering valve opening only after the exhaust port has closed, operating means for said valves including a cam operatively associated with each of said valves and followers coacting with the cams and valves, a governor, the followers and cams being arranged for relative displacement by the governor under influence of changes in an engine operating condition, the operating means associated with one of said valves being of differing regulable valve-opening and closing characteristics such as to provide different durations of opening of the associated valve, and further such as to provide for a relatively earlier and later valve opening and a differentially earlier and later closing, under the regulating influence of the governor, the operating means for the gas and air valves being relatively timed to effect substantially sequential operation of the metering valve and admission valve, whereby the air, supply is accurately metered in the cylinder shortly prior to gas introduction thereto, and the valve operating means further being timed for effective air metering and gas admission, following closure of the exhaust port.

2. In a gas and air control assembly for a twocycle engine supplied with a true gaseous fuel, as herein dened, a gas admission valve, piston controlled air supply and exhaust ports, an air metering valve, a pair-of cams, one for actuating load conditions to close the air metering valve atV least as early' as opening of the gas admission valve, and to provide for opening of said Ygas valve only after the exhaust port is closed, and close to the beginning of compression, a governor, a connection from the governor to the followers for Vshifting the followers axially with respect to the cams, the gas valve cam being characterized by a profile or nosewhich is arranged to engage the associated follower` in later timed relation at low engine loads and relatively earlier timed relation Y loads.

area encountered by its follower at higher engine 3. In a two-cycle internal combustion engine assembly, a cylinder, a piston operable therein, said cylinder having a port for admission of 'scavenging and combustion air, means for supplying to the engine a fuel of true gaseous type including a fuel admission valve and an exhaust port, both ports controlled by said piston, separate valve means coacting with the cylinder and piston for metering the air charge in the cylinder reffective only after closure of the exhaust port by releasing a predetermined portion of said air charge, engine-timed means for regulating the 15, portion of air thus released in `accordance with at high engine loads,. and lwhich is further de- Y signed to leave the follower later at lower engine loads and earlier at higher engine loads, as the follower is influenced by the lgovernor correspond- Y ing to the variations in engine operatingconditions, the air-metering valve-operating cam bee r ing characterized by a prof-lle or contour which is of greatest effective width Vin its area encountered by the associated follower at relatively lower engine loads and of lesser effective width in the requirements of engine load and for regulating a succeeding fuel charge next to be admitted for combustion, and engine actuated means operable substantially sequentially and in substantially f uniformly timed relation to said air charge metering means for metering andadmitting to the air charge, after complete admission of combustion air and accurate air metering, a charge of said gaseous fuel through the fuel admission valve to the cylinder, said last means being responsive, i

as to admission of fuel quantity, to current engine load condition. Y

HENRY SCHRECK; 

